Rotary drilling mechanism



April 6, 1937.

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Patented Apr. 6, 1937 UNlTED' STATES PATENT OFFICE] K273221235???Application June 16, 1931, Serial No. 544,863 20 Claims. -(o1.2s4-1se)This invention relates to drilling and has for its principal object theprovision of apparatus for rotating a drill pipe while suspending thedrill stem by hoistingmeans .connected with the ro- 5 tating means, bothbeing hydraulic, whereby the changes in resistance encountered-by thedrill bit transmission embodying two separate units, a variable deliveryfluid pump of the tilting box type and a variable speed hydraulic motor,in one and mounted on a substantially stationary multiple.

cylinder barrel and shaft thru which stationary members the propellingfluid is delivered to the cylinders thru a distributing plate attachedto and revolving with the drum.

Another important object is to eliminate the pressure between therubbing surfaces of the piston and cylinder walls due to centrifugalaction which is considerable at high speeds in rotary barrel multiplecylinder pumps and motors. I accomplish this by making the barrelstationary 0 thus eliminating all but the reciprocating motion in thepistons and in order to get the necessary relative turning motionbetween the barrel and shell I allow the latter to turn.

A further object is to eliminate all gearing betweenthe motor and thework by providing the 'revolving shell with various means so that it canbe used directly as a hoisting drum, traction wheel,

winch capstan etc.

A still further object is to provide means for 40 more rapidly coolingthe propelling fluid as it passes thru the pump which I accomplish bythe provision'on the revolving drum shell of the pump as well as on aportion of the drum of the motor of heat radiating fins which increasethe transfer of heat thru the shell to the cooling air. Thetransmissionof power thru any medium is found to be attended with a.loss of energy by friction in ,the form of heat and the emciency oftransmission is often limited by the speed of dissipation of this heat.In the old stationary casing pumps and motors of the type with whichthis application is concerned, it is apparent that the rate ofdissipation of heat as compared to mine is very much lower since thereis no relative move I movement of the larger motor.

and the heat radiating surfaces except of course the small movement dueto convection. Where the radiating surface as in this type of hydraulicmachine is solarge as compared to the fluid contacting surface it isquite important that the ra- 5 diating surface be given movement, andalso the provision of flns on a moving surface is of much greaterrelative importance than the provision of fins on an equal stationarysurface. In order to still further increase the cooling efllciency thefins may be provided with propeller or fan-like portions which break upthe atmosphere that tends to revolve with the drum and also to increasethe movement of the cooling air.

A further object of the invention is the provi- 15 A still further andimportant object of the pres- 25 ent invention is the method of couplingtogether two hydraulic pumps with two hydraulic motors so that both ofthe pumps can operate one of the motors when required, where undernormal operation one pump operates one of the motors and in the pipingbetween the pumps excess or diminished pressure actuates mechanism whichcontrols the angle of the tilting box in the second pump which in turncauses a relatively small The mechanism just recited also lends itselfreadily to hand operation since in ordinary drilling the stem is notraised but is lowered as in the judgment of the I operator seemsproper.

Other objects of the invention have to do with the specific design ofthe various parts all of which contribute to the provision of a powertransmittingsystem which obviates the use of brakes and permits analmost instant'ohange of direction of rotation of the motor unit withoutthe slightest shock and which permits in case of drilling the buildingof the draw-works into a self-contained piece which can be positioned inthe derrick as a unit so that in moving the unit from place to placethere are no loose parts to be fitted to the derrick such as posts andhead boards.

In previous devices for control of the pressure upon the drill bit bycooperation between the rotating and hoistingmechanisms the method ofcontrol has been thru changes in the strength of the electric current orby purely mechanical means. The present invention contemplates theelimination of all electrical equipment between the rotating andhoisting means and substituting for the mechanical means ofinter-relating the driving and hoisting means of pipe lines conveyingthe oil of an air-tight closed system from a plurality of pumps to aplurality of means, the latter including a hydraulic motor for rotatingthe drill stem and a larger motor for raising and lowering the drillstem. The principal advantages gained by the use of the hydraulicdraw-works of the present invention are case of operation, assurance ofa straight hole, elimination of danger to the workmen because of abruptstops and step-by-step gradations which are here eliminated, greatlydecreased cost of inspection and repairs, and capacity to run for longperiods of time without attention while preserving a definite andabsolute control of the torque on the rotary and of pressure at the endof the bit, eliminating respectively the many fishing jobs which arerequired by reason of the twisting oil of sections of the drill pipeandthe variations from vertical in the drill-v ing of the hole whereinemcientcontrol of pressure at the end of the bit occurs.

In the drawings: Figure l-is a plan view of the lay-out, being partlydiagrammatic to show the control system.

Figure 2 is a side elevation. Figure 3 is a vertical axial section thruthe hydraulic motor which is the drum.

Figures 4 to 8 are sections taken on lines 4-4, 5-5, 6-6, 1-1, and 8-8,respectively, of Figure 3.

Figure 9 is a fragmentary section taken on line 3-9 of Figure 8.

Figure 10 is a vertical axial section thru the variable delivery pump.

Figures 11 to 15 are sections on lines H-|l, l2-l2, I3l3, "-44, andl5-l6, respectively, of Figure 10.

Figure 16 is a vertical axial section of a modifi- 5 cation of themotor.

Figure 1'7 is a vertical axial section of the control valve.

Figure 18'is a detail. In order to give a comprehensive idea of theinvention I will first describe its general application in a welldrilling control system such as diagrammatically illustrated inFigure 1. In this figure the rotary I0 is shown as driven by hydraulicdrill motor i2 which receives its power by 5 supply and return pipes l4and I5 via the fourway valve i6 either from variable delivery drill pumpl8, a second-four-way valve I 3 being closed, or from variable deliverypump 26, bothvalves l6 and I! being open, these pumps l3 and 2lbeingarranged so that these may be driven independently or by a common primemover as will be more fully described hereinafter. The hydraulic hoistmotor 23 is connected to the supply pump 20 by pipes 2| and 22 which arealso connected to mains l4 and i5 thru valve l9.

The drill motor I2 is controlled by means of a four-way valve 24 movedeither manually by handle 25 or automatically by pressure chamber 26.The valve 24 communicates on one side with two pipes 21 and 23 betweenthe mains I4 and I5 at point 23 and on the other side with pipes 30 and3| to the control cylinder of pump l8; one

end of the pressure cylinder 26 of the valve 24 being connected by pipe32 to the mains l4 and ii at shunt 33, the other end being open to theatmosphere 45 (see Figure 17).

The hoist motor 23 is controlled substantially in the same manner asmotor l2, that is, by' valve 34 which, like valve 24, is connected onone 6 side to mains 2| and 22 by pipes 3'! and 33 at point 33 and on theother side to the control end of pump 20 by pipes 46 and 4|, but unlikevalve 24, which has an automatic control that is responsive only to thefeed pressure of the motor 10 i2, the valve 34 has a control that is notonly responsive to the feed pressure of hoist motor 22 but is alsoresponsive to the feed pressure of motor l2 as well. This is adifferential control and is accomplished by connecting one end of the 16pressure cylinder 36 to the mains 2i and 22 with pipe 42 at shunt 43 andconnecting the other end of cylinder 36 to mains l4 and i5 at shunt 44by means of pipe 45. The shunts 33, 43 and 44 are each provided with twovalves in order that 20 pressure may be maintained in the control valvecylinders 26 and 36 regardless'of the direction of fiow in the mains. I

The main shaft 46, mounted in bearings 41, is driven in any preferredmanner as, for example, by an electric motor mounted directly on theshaft but as I prefer it and as illustrated this shaft receives powerthru a sprocket wheel 46 connected by a chainto a source of motive power48 which may be gas, electric, steam, or water 30 driven. The hydraulicpump 26 is directly secured to the main shaft 46 by the coupling 66 andfollows standard practice, the angle of the tilting box being governedby the position of. valve 34 as will be more fully set forth herein- 35after.

The cathead shaft 5| is mounted in bearings and has at either endtheusual cathead drum. This shaft receives its motion thru sprocket wheel62 connected by a chain 53 with sprocket wheel 64 40 which may be causedto rotate with the main shaft 46 by the clutch 55. It will be noted thatthis chain 53 is the only chain used in the mechanism except for theoptional chain to the source of power which is only used in case themotive 45 power is not directly applied to the shaft.

The pump 20 discharges oil under pressure to the hydraulic motor 23which is the hoistin drum, the discharge pipe being 22 and thecorresponding return pipe being 2|. It is extremely so important thatthe oil within the system shall fill all of the space except thatoccupied by the metal and it is equally important that the oil shall befree of air or other gas that is compressible. To this end I followestablished prac- 5n tice and position an oil reservoir 56 above the oillevel in the pump and the motor and while I shield this reservoir fromdust and dirt by means of the cap 61 I maintain communication with theoutside air in order to preserve atmospheric ca pressure within thereceptacle 66.

Considering particularly, Figure 2, the discharge pipe 22 from the pumpleads thru a passage 69 to the vertical pipe or passage 60 at the leftof the center of the drum while the return 65 pipe 2| communicates withthe right hand vertical pipe 6| thru the horizontalpipe 62. When thevalve34, and therefore the tilting box of the pump 20, is in neutralposition no oil is pumped thru pipe 22 and the hydraulic motor 23 isthere- 7c fore stationary since no oil is fiowing and consequently nomovement of the drum is possible.

A slight movement of the valve 34 changes the angle of the tilting boxof the pump 26 and causes a very slight amount of oil to be pumped 7g byeach of the pump pistons giving a slight but constant torque on the drumas will be described later. The pump 20 may be of standard manufacturebut I prefer to use one of the type developed by me and to be describedfarther on in the specification.

Without describing at this time the detailed construction of thehydraulic pump 20 and motor 23 which forms the hoisting mechanism of thedevice I will now describe the general operation. Drilling. Automaticcontrol: First open valve l6 and close valve l3. Next start pump 23 andadjust the control valve 34 so that motor 23 will exert enough torquethru the hoisting drum to support most of the weight of the drill stemallowing the balance, a certain predetermined weight, to rest on thedrill bit. The relative amount of weight taken by the drill bit and bythe hoisting drum is governed by standard and well known practice andpermits extremely fine changes in actual pressure by the cutting end ofthe drill stem on the material encountered. The third step is to openand adjust control valve 24 so that pump l6 starts and drives motor l2and thus rotary it at any desired speed.

The pressure in main l4,'proportional to the load on motor I2, isreflected thru the pipe 45 to one end of the pressure cylinder 36 ofvalve 34 which tends to cause the latter to allow an increased flow offluid to the control end of pump 20 and thus increase the torque ofhoist motor 23.

But this reflected pressure in cylinder 36 is opposed and balanced bypressure in the opposite end reflected from main 22 so that the motor 23still exerts the predetermined pullor lift on the drill stem. However,if the drill bit should strike a hard strata or-should become wedged andthus increase the load on motor l2 to a greater extent than determinedby the original setting of the valves 24 and 34 a back pressure willbuild up in line l4 and from there will be transmitted to both controlcylinders 26 and 36. The increased pressure in 26 will unbalance theforces as determined by the original setting and cause valve 24 to allowpump 16 to increase its delivery of power to motor I2 to take care ofthe increased load. The increased pressure in 36 via pipe 45 willoverbalance the opposing pressure in the cylinder due to the linepressure from main 22 transferred to the cylinder by pipe 42. Thisoverbalance will move the valve 34 in a direction to cause pump 20 toincrease the power delivered to motor 23 which in turn will liftthedrill stem but only an amount necessary to relieve the overload on motorl2. Of course as soon as this occurs the valve 34 is automaticallyturned again to its original setting since the two pressures deliveredby pipes 42 and 45 will have returned to their original canceling valuesand the predetermined rate of drilling will be resumed until furtherobstacles are encountered by the drill bit.

There will be an opposite effect on the control valves .24 and 34 if thebit strikes a soft strata since this takes the load off motor l2 andincreases the load on motor 23. No load on the former means low pressurein'main l4 and thus in pipes 32 and 45. Low pressure in 32 causes valve2,07o,iss

Drilling. Hand Control: First open valve l6 and close valve I! as in theautomatic control. Next start pump l8 and operate valve 24 by hand lever26 until motor I2 is driven at-the desired speed. 'I'hirdly, start pump23 and by means of hand lever 35 cause the pump to deliver enough powerto motor 23 to suspend some of the weight of the drill stem allowing therest of the weight to force the drill bit into its work. -If desired thepump 26 and motor 23 may be stopped entirely and the drill may be feddownward by means of the band brake I9 and handle 20'. It will be seenthat this operation is very similar to the automatic control and differstherefrom only in that the valves 24 and 34 are no longer responsive topressure since pressure lines 32, 42, and 45 are shut oif which permitsthe valves24and 34 tobe controlled entirely by means of hand levers 26and 35. The sensitiveness of hand control will, of course, depend on theability of the operator to respond to the reactions of the drill motorI2 and in most cases the automatic control is much better. But fordrilling thru soft strata hand control is preferable. l

It will be apparent that valve 24 may be left under automatic controlwhile valve 34 is operated by hand or vice versa.

Hoisting: Since the drill stem is lifted entirely by means of motor 23it is necessary that motor l2 should be shut down which is done byclosing valve l6 and setting pump l8 on neutral or stopping the pumpentirely by throwing out clutch 53 on main shaft 46. Then bymanipulating handle 35 the valve 34 may be turned so as to supply enoughpressure to the control end of pump 20 to cause the latter to deliverthe amount of oil necessary to drive the motor 23 at the desiredhoisting speed. In raising long heavy drill strings it may be necessaryto use both pumps in which case valve I9 is opened and pump I8 isadjusted to deliver power in parallel with pump 20.

Referring now to Figure 3 which shows a vertical section generally thruthe axis of the hoisting drum. The two frame pedestals 63 and 64 supportthe device but it must be remembered that the large portion 66 of theshaft of this motor does not revolve in the bearing of 63 but on thecontrary the shaft 66 is held stationary by a plurality of keys 61 whichare purposely made not too tight fitting; The bearing in the pedestal 64on the other hand is a rotatable one and the part supported is the righthand end of the revolving shell which latter in turn supports thestationary torque shaft 10 in self-adjusting roller bearings H housed inthe hub 12 of the rotating angle box 13. The central stationary piece,which is substantially if not actually integral and consists of theported shaft 66, the solid torque shaft I6 and the cylinder barrel 15,is supported at the left in the pedestal bearing 63 to which it iskeyed, and at the right by the bearings I I. It is very important thatthis stationary unit shall maintain the left hand plane face of thecylinder barrel precisely parallel to the engaged face of the rotatingportion of the motor, this being true of all devices of this kind.

Considering first the parts that have no rotation,-the larger shaftportion 66 is closed at'the leftas seen in Figure 3 by a pipe flange l1tapped to receive the two oil pipes 60 and 6| which are -merelyhorizontal continuations of the previously mentioned vertical pipes 60and 6| and consequently bear the same numerals. Surrounding the largeshaft 66 and in engagement with the pipe flange 11 are shims ill, thenumber of which will be varied to secure the desired pressure adjustmentbetween the cylinder barrel and the revolving valve plate, thisadjustment being arranged thru the keys which, as before remarked. mayhave movement axially of theshaft, and by a ring I! which engages theouter case". The adjustment may be obtained by means of a plurality ofadjusting screws (not shown) spaced around 'the flange II and actingeither on the shims II or directly for moving the keys inward againstthe ring I! to keep the desired pressure on the case ll between whichand thesimilar inner case II are a plurality of helical springsequi-spaced about the shaft 86. These springs, which will vary in sizeand strength with the different sizes of motor, are arranged with theiraxes parallel to the axis of the shaft 86. The spring nest 82 is notneeded when the drum is being revolved but it is very important when thedevice is not under load as these springs, whose total strength is verymaterial, preserve always the needed firm bearing between the valveplate and the cylinder barrel.

Inward of the spring nest and its two cases are the roller bearings uponwhich revolves the valve plate 80 to which is secured the annularclosure 88 which has an oil tight engagement with the ring 19. Insteadof the packing shown in Figure 3 I may use an arrangement similar tothat 3 illustrated in Figure 10 which will be described farther on inconnection with the pump unit, therefore in Figure 3 in several places Ihave purposely omitted the packing for the sake of clearness ofillustration but it will be understood that 35 the device is made as oiltight as possible at every joint.

The barrel is a relatively short cylinder of solid v metal having withinit a plurality of piston receiving cylinders 88 each having one or moreports I1 somewhat radially outward from its axis. Near the left handend, as seen in the figure, there are ports 02 and 32 opening in fanshape from the passages "I and CI in the solid metal of the shaft 08 andthe barrel ll. Since these passages are mere continuations of the pipesl and GI they have been given the same numeral for the sake of clearnessso that the numeral SI may be considered the entrance passage for theoil from the pump 20 via the horizontal, pipe section 22. It will benoted that the radius of the arc of the segmental port a: isconsiderably greater than the "radius of the similar arc of thesegment-shaped port 33 so that these two ports may communicate with whatcorresponds to the elongated ports of the typical valve plate which ishere varied materially in order to secure greatly increased strength andto avoid the noticeable hoop tension in the walls of the usual-valveplate.

At the right hand end of the barrel I! is the angles to the axis of thetrunnions as both axes I lying in a single plane, here positioned at anangle from the vertical. I preferably provide bushings between the shaftand the trunnions it and on the keys 61 and thus providing ready meanstorque shaft III which ends just beyond the marbetween the socket ringand the trunnions OI. Two trunnions are integral with the trunnion blockI" and two other trunnions are formed at the ends of a pin driven thruthe trunnion block so that the non-rotating socket ring has movementabout the stationary torque shaft as would a disk which is rockinglymounted at its center upon a point so that the point of dip runs aroundthe circumference but the disk has no angular motion about. the point.Such motion is common in this art but the present device differs fromother motors in that in this case it is the torque shaft which isstationary and it is the angle box which rotates.

The swash-plate or socket ring 98 may be a twopiece ring as shown inFigure 10 and as described later on in connection with-the pump but inthe modification shown in Figure 3 is a one-piece ring having hubs IIIIto surround the trunnions and being cut away as at I02 to clear theenlarged yoke section of the torque shaft III. In this ring are aplurality, in the present case seven, nearly equi-spaced sockets eachreceiving a bushing I02 cooperating with an intermediate bushing I and athreaded bushing I05 to receive snugly the spherical end its of theconnecting rod I01, the other spherical end I08 of which is received inthe piston I09 in quite similar manner, again following usual practice,my desire being that the fit of the piston in the cylinder 88 shall beso perfect that I require no rings or packing. The pistons and cylindersare ground and lapped to a smooth working fit and I prefer to follow theapproved scheme of cutting narrow and shallow grooves around each of thepistons, preferably having at least three such grooves in each piston soas to trap dirt and also break the fluid leakage lines. o A

The principal rotating parts are the valve plate 80, the drum itself,and the angle box 13, these three parts being substantially integral butactually formed as three separate units which are securely but notpermanently secured together since it is desirous of having convenientaccess to the interior of the drum for repairs and adjustments. Thespooling drum is a hollow cylin der having right angular flanges III]and III to which are secured respectively the flange 2- of the angle boxI3 and the flange iii of the valve plate, the line of bolts beingdiagrammatically represented-by the numerals I. The outer cy-'-lindrical surface of the drum may be and preferably is grooved as at iiito fit the size of rope I la (see Fig. 18) It is desired to use ropeusually somewhat in excess of an inch in diameter and normally perhapsslightly less than half a mile in length.

The angle box is somewhat hemispherical between lts flange I I2 and itshub I2. The angle of this box corresponds exactly to the angle of thesocket ring, that is, for example, about 20 or 30 from vertical. Theangle box which revolves about the axis of the shaft "-10 is providedwith thrust and roller bearings II I and III in suitable races onemember I20 being common to both. The hub 12 of the angle box 13 hassecured to it at the right hand end in Figure 3 a drum closure I2Iintegral with an outwardly extending shaft I22 supported by outboardroller bearings I23 in an outboard bearing box I25 which in turn isclosed by an outboard bearing closure I28 having a grease inlet 'valveI21. The outer race of the bearing I23 is made floating to allow for thenecessary but extremely slight axial and angular movements of therotating parts.

posed passages I33 with the inner port I34 which in turn communicateswith the'port 83 in the cylinder barrel. n the other semi-circular halfof the valve plate the groove I48 corresponds with I38, the ports I aresimilar in size and position with the ports I3I but the radial ports I43are considerably shorter than the corresponding ports I33 since theformer lead to the port I44 which communicates with the port 92 in thebarrel.

An important feature of the invention is the continuance of the portsI34 and I44 as shallow grooves I38 and I45 respectively, these twogrooves together insuring that the oil under pressure shall at all timescompletely encircle the contacting faces of the valve plate and cylinderbarrel thereby relieving these two faces of the huge pressure exerted attimes by the reaction to the thrust of the connecting rods I81. SpaceI41 provides a clearance between the valve plate and the casing. Thesmall round ports are used for strength, otherwise the port wall wouldhave to be very heavy because of the large radius of the port walls fromthe center.

The operation of the drum is believed to be quite apparent, the actionbeing as follows:

Upon increase in pressure in the pipe I4 and therefore in the controlpipe 45 connected thereto, the control valve 34 of the pump 28 isoperatedin a manner described below, thereby causing a slight additionalamount of oil to-discharge from the pump 28 thru pipe 22. Thisfluid-continues thru the passage 88 in the larger shaft portion 88 ofthe stationary member of the drum, passes upwardly in Figure 3 and tothe right as in Figures 4 and 5, passing into the segmental shaped port82 of the cylinder barrel and from thence into the alined port I44 atthe right of Figure 4 and in the upper half of Figure 3, from herepassing thru the radial passages I43 to the series of ports HI andpassing from here into the alined ports 81 leading to a plurality of thecylinders 88, causing these pistons I88 to move to the right in Figure 3which movement causes the upper end of the socket ring to move to theright, this in turn causing a rotation of the angle box so as toincrease the tension on the hoisting drum rope.

While this action is takingplace the lower portion of the socket ring 88is moving to the left as seen in in Figure 3 and this forces oil thruthe lower ports 81 in the cylinder barrel to the alined port I3I in thevalve plate, the oil from here passing radially inward thru the portsI33, then thru the port I34 in the valve plate to the fan orsegment-shaped port 83 in the cylinder barrel, this port beingconstantly in communication with the passage 8| which leads to the oilreturn pipe 82, returning the oil thru the pipe 2| to the pump 28. Thisis the normal drilling operation but when it is desired to raise theentire drilling stem, the valve I3 is opened and the valve I8 closed. Inthis way the rotary drum 23 is driven by the combined action of thepumps 28 and I8, mypreference being that the pump 28 shall be of saytwice the power of the pump I8 and that the drum 23 for full power shallrequire the combined horse power of the pumps 28 and I8, whereas theneeds of the motor I2 shall always be satisfled with the delivery offluid from the pump I8. When raising the stem the stop valyes in theauxiliary lines 32, 42 and 48 are closed when the valve I8 is closed andthe tilting box control valves 24 and 34 are operated by hand to givethe required speed to the drum.

The improvements pointed outin the above description of my hydraulicmotor are also present in my variable-delivery pump as will be apparenton consideration of Figure 10 which is a central sectional view of thenew pump. As in the motor the pump is provided with a stationarycylinder barrel 18 which may be integral with the shaft 88 as in themotor but for large capacity machines is preferably made separate andprovided with a large central bore for fitting over the reduced end ofshaft 88 to which it is keyed.. The barrel has a plurality of cylinderbores 88 parallel to the axis of the stationary shafts 88 and 18 andcommunicating by cylinder ports 81, valve plate ports I38, I3I andbarrel ports 82 and 83 with the passages 88 and 8| .of the shaft 88.Each cylinder bore 88 carries a piston H8 fitted with a connecting rodI81 having spherical ends I88, working in a socket ring of two pieces-I88--I8I clamped about the ends I88 and mounted to wabble on the mainstationary shaft 18' by means of a universal Joint as in the motor.

Between the two parts I88 I8I of the socket ring are clamped thebushings fitting the trunnions 88 and there are also clamped the splitbushings I82 against the bushings I83 which provide sockets for the endsI88. The part I8I has the same thrust and .side bearing structure as thesocket ring described above in connection with Figure 3 and thereforecooperates in the same manner with the roller bearings H1 and H8 mountedin the tilting box I84.

However, while in the motor of Figure 3 the axis of'the drum with whichit turned in the case of the pump as shown in'Figure 10, the angle isnot fixed but is made adjustable by mounting the tilting box I84 to turnon diametrically positioned trunnions I88 which are studs screwed intothe casing I88 and provided with sockets I81 so as to be replaced andadjusted from the outside of the casing (see Figure 15). On the two endsof a diameter perpendicular to-thatpassing thru the trunnions I88 areprovided lugs I88 which are preferably integral with the tilting box I84and to which are connected, either by ball and socket joint orotherwise, the connecting rods I81 socketed at their opposite ends inthe control pistons I88 mounted in-cylinders I88.- As shown in thedrawings the cylinders I58 maybe integral with the revolving casing I88as well as integral with the auxiliary casing I88 which fits over theportion I82 of the inward extension I83 of the valve plate I84; theauxiliary casing, however, is slightly spaced at I88 from the remainderof the extension I83 as well as from the barrel 18 most of, which. ittelescopes. A connection with the pressure lines is provided for eachcylinder I89 one of which may be traced from the cylinder end-at I81along the casirfg at I88 down tionary stuffing box I18 where a threadedbore 48 provides means for connection to a line 48 leading to one of thefour way control valves 24 or. 34. The other pressure connection may betraced from the lower cylinder I58 in a similar manner to bore H in thestufling box I18.

Itwill readily be seen that the positions of the control pistons I58determine the angle of the tilting box I54 and that by varying therelative pressures onthe control pistons the stroke of the pump pistonsmay be positively adjusted. Therefore by means of one of the abovementioned four-way control valves, I connect the control cylinders I58to the previously described pressure mains I4 and I5 (or 2I and 22) andthen by moving the valve and admitting oil under pressure to thecylinders I can determine the delivery of the pump, the casing I58 ofwhich is driven at a constant speed by means of a gear or pulleyconnected on the end I18 of the driving shaft I14. Instead of connectingthecontrol cylinders to the pressure mains I may connect them to aseparate source of control pressure thus making the control independentof the pressure in the mains which may be desirable for starting thepumps from neutral when the pressure in the mains is too low to move thepistons I58 but after starting the pump the pressure lines may be againconnected to the mains if desired.

Referring to the left hand side of Figure 10, it will be seen that theannular valve plate I84, surrounding shaft 88 and engaging the verticalsurface of cylinder barrel 15, is integrally supported on the end of thecylinder-like projection I18 of the drum closure I88 which is bolted tothe drum or casing I58 by means of bolts II4. Within the cylindricalprojection I18 are the roller bearings 85 held in inner and outerannular races I82 and I83, respectively. The outer race I82 is heldagainst a ring-like projection I84 on the rear of the valve plate by thecylindrical projection, I85 of the annular closure I88 bolted to thedrum closure I88. Within and spaced from the projection I85 and engagingthe stationary shaft 88 is a nest of springs 82 held between twof'rings88 and 8|, the latter of which engagesithe racev I88, Asfully describedin connection with Figure 3 the tension of the springs is adjusted bymoving the condi- 1a to the right either by shims 18 between flange 11and keys 81 orby screws projecting thru flange 11 into engagement withthe keys 81. The closure I88 also carries a stufilng box I88 withinwhich is the leather U-packing I88, filler ring I88 and packing glandI8I all of which make an oil-tight closure for the casing. If any oilshould leak by the inner annular lip I82 of the valve plate and find itsway to the ball races it would not force its way out thru the stuflingbox 188 because passages I88 are provided for draining it into thecasing by way of the above mentioned space I85 between the casing I88and the plate and barrel. As I intend to have all space filled with oilit will be seen that additional leakage into the casing I58 will raisethe pressure, therefore two ball checks I85 are provided for relievingthis pressure. Two checks are provided (one in each main I4l5 or 2I-22)in order that there will always be a low pressure main connected to theinside of the casing, for example,

by wayof passage I88 regardless of the direc-' tion of flow. As will beseen in Figure 10 I locate these check valves at the end oi the boresI4-I5 and by providing the set screws I81 with kerfs or sockets I88 I amable to set or to adjust the valves from the outside by means of a longshanked socket wrench I88 which I insert thru a. hole in the manifold 11which hole, of course,

is ordinarily plugged.

In order that the heat from the transmitting fluid may be quicklydissipated I provide radiating fins 28I onthe revolving casing I58 andfor protection of the workmen enclose the whole in a perforated casing282.

Referring to Figure 16 wherein is shown a modification of the motorillustrated in Figure 3 it will be seen that most of the parts areidentical with my improved pump described in the preceding paragraphsfrom which it differs essentially only in replacement of the tilting boxI54 by the stationary angle box 18 of my other modification and, ofcourse, the absence of the control cylinders and pistons as well as theelongated stufflng box I18. The drum is substantially the same as thatof Figure 3 but in order to provide additional means for taking powerfrom the motor I use an extended shaft I14 having means at I18 forattaching a pulley. sear, coupling or any other power transmittingdevice.

In some types of work it may be desirable to build the gear or. pulleydirectly on the drum, also in traction work the drum may constitute thehub of the driving wheel.

Altho most any one of several types of presure responsive valves 24-44may be used in my system diagrammatically shown in Figure 1, I preferthe one shown in detail in Figure 17 which comprises two main parts, afour-way valve 24 and a pressure cylinder 28, the latter being dividedinto two expansible chambers 2I8 and 2 by the reciprocating piston 2I2provided with the usual air-tight or fluid-tight gaskets 2 and 2I5. Thecompartment 2I8 is provided with a port 32 for connection to pressureline 82 while compartment 2 has a port 45 which maybe either connectedto a pressure line 45 as is cylinder 88 of Figure 1 or may be left opento the atmosphere as is cylinder 28 of Figure 1. The piston 2I2 iscarried on rod 2I8 connected at one end to the hand lever 25 and at theother end to the piston 2I1 of the four-way valve 2|.

The piston 2" as well as the piston 2I2 are biased to an upward positionpartly by the hand lever 25 but mostly by the spring 2I8 on which thepiston 2I1 rests. The tension of this spring 2I8 therefore provides away for adjusting and adapting the pressure cylinder to operate withsystems of difierent pressures and with different connections, forexample, if port 45 is to be left open to the atmosphere as is the casewith cylinder 28 of Figure 1 the spring tension should be made large tobalance the pressure in line- 82 but where both ports are connected topressure lines as are 42 and '45 of cylinder 88 the spring tensionneednot be so large. A ready means for regulating the spring tension isprovided by the plug 228 in the base of the four-way valve. The usualstufilng boxes are provided at 22I, 222 and 228 so that no oil will leakout around the piston rod.

The operation of the valve will be apparent when considered with thedescription of the operation of the system as a whole given near thebeginning of this specification.

Certain details and instructions have purposely been omitted from thisspecification but will be apparent to those skilled in the art and towhom the specification is addressed, for example, in all such mechanismsit is necessary to provide relief valves to keep the oil pressure fromrising ab ve that which is necessary to overcome normal resistance inhoisting and consequently such valves are to be added to the presentdevice being such, for example, at 1100#, the valves-being merely springpressed check valves preferably of the type where the pressure can bealtered. Upon excess pressure the oil escapes from the high pressureport passage into the drum space and from here passes into the lowpressure port thru a suitable check valve. What I claim is:

1. In combination, a hydraulic pump of the type having a tilting box, achange of angle of which causes flow of fluid from the pump in chosendirection and amount, a hydraulic motor l5 cooperating therewith havingan angle box characterized by the barrel of the hydraulic motor beingstationary while the shell is flxed to and revolves with the angle box,said shell forming a hoisting drum, and a fixed shaft secured -to thebarrel and serving as a support for the barrel and the shell, said shafthaving bores therein for tgonducting operating fluid to and from the mor.

2. A brakeless hoisting drum for drilling operations, consisting of ahydraulic pump motor unit in which the motor and the pump are of theswash plate type, said pump and motor each having a stationary pistonbarrel, a revolving shell enclosing said pump, a revolving shellenclosing said motor, an angle box carried by each shell, means on thepump shell for tilting the angle box carried thereby, a control rod forcontrolling said meansto vary the stroke of the pump pistons, the angleof the sdck'et ring of the motor being constant, the pistons of themotor acting as a drum brake in response to changes in position of thecontrol rod of the Pump.

ii a hydraulic motor hoisting drum, astationary shaft consisting of anend section having a pair of fluid passages there'thru, a barrelsubstantially integral with said shaft, and having ports communicatingwith said passages, and a torque shaft, a socket ring oscillating abouta trunnion block carried by the torque shaft, pistons reciprocatingwithin the barrel, connections between the pistons and the socket ring,and a revolving unit mounted to turn about said stationary shaft andconsisting of a valve plate, a

drum and an angle box.

4. In a hydraulic motor hoisting drum, a valve plate, a cylinder barrel,communicating ports in said barrel and'valve plate characterized by theends of each of the ports being continued annularly about one of thecontacting faces as a shallow groove, thru whichthe fluid under pressuremay circulate to reduce the friction betweenthe valve plate and thebarrel, a valve plate port consisting of an arcuate shallow groove, aplurality of axial bores extending from said shallow groove, a portradially inward from said bores and in communication therewith.

5. A valve plate having on each half an arcuate groove, having'lnone-half an arcuate port of a chosen radius and having on the other halfan arcuate port of different radius, and radially disposed channelsestablishing communication between said grooves and one onlyof saidports at each side. 7

- 6. A hydraulic motor, the outer shell of which is a hoisting drum, acylinder barrel, a socket ring having oscillating movement with respectto the cylinder barrel, an angle box fixedly secured to and forming oneend of said drum, a

75 valve plate secured to and constituting the other end of said drum,and means for holding the cylinder barrel against rotation, said meanscomprising a drum supporting bracket and a shaft secured to the bracketand to the barrel.

7. In a hoisting drum revolving motor, a cylinder barrel, a shaftsubstantially integral with the cylinder barrel, a valve plate mountedto revolve about the shaft, distributing ports in the rotating valveplateand fluid passages thru the shaft and the cylinder barrel fordelivering fluid from a pump to the distributor ports in the valve plateand from thence to the cylinders of the cylinder barrel. 1

8. A constant stroke. swash plate type hydraulic motor in which thetrunnion block has a fixed angle, of oscillation and the outside shellof the motor revolves while the cylinder barrel is held stationary andan angle box fixedly secured to said shell and cooperating with thetrunnion block to maintain said fixed angle. I

9. In a hoisting drum, a stationary torque shaft, an angle box having ahub rotating about the axis of the torque shaft, a roller bearingbetween the end of the torque shaft and the hub, a shaft extending fromthe angle box, a stationary frame, and a floating roller bearingsupporting the end of the angle box shaft in said bearing.

10. A shaft, a valve plate, a cylinder barrel substantially integralwith said shaft, a roller bear-,

ing between said valve plate and said shaft, a frame, a key engagingsaid frame and said shaft to prevent rotation of the shaft, 9. springnest to resiliently hold the valve plate against the cylinder barrel,and means including said key for altering the pressure exerted by saidspring nest.

11. The device of claim 10 in which the spring nest consists in aplurality of helical springs placed annularl'y about the shaft withtheir axes parallel to that of the shaft.

12. A valve plate having two spaced ports,.one on either side of adiameter to establish communication with the cylinders of a cylinderbarrel, said ports being characterized by the provision ofspaced-barscommunicating with a shallow groove in the faceof thevalve'plate and communicating thru separated passages with the intakeand exit ports, whereby the strength of the valve plate is greatlyincreased over that given by a single opening port.

13. In a well drilling system, a hydraulic pump,

of the swash plate type, a stationary cylinder barrel, 9. swash platecarried by said barrel, a revoluble shell coaxial with and enclosingsaid barrel and plate, an angle box plvotally supported by said shell, apair of cylinders and pistons therein carried by said shell, saidpistons being connected to diametrically opposite points on said anglebox whereby the relative positions of said pistons control the angle ofsaid box, a pipe connection between one of said pair of cylinders andthe pressure side of said pump and a second connection between the otherof said pair and the return side of said'pump and means in said pipeconnection for regulating the pressure between the pump and thecylinders whereby upon the rise of pressure to a predetermined limit thepistons are moved to change the angle of the angle box to thereby reducethe stroke of said pump.

14. In a well drilling system, a hoisting drum comprising a pair ofspaced alined supports, a

stationary shaft carried by one of said supports,

of said supports, a cylinder barrel secured to said stationary shaft andlocated in the opposite end of said drum, and having a projectionjournaled in said drum head, a swash plate trunnioned in said shaft, andan angle boxcarried by said drum.

15. The device of claim 14 in which said stationary shaft is providedwith passageways for carrying fluid to and from the cylinder barrel. 16.The device of claim 14 in which said stationary shaft has a central boreextending thru said barrel and to said swash plate, a bore on each sideof said centralbore acting as conduits for transferring fiuid to andfrom said cylinder barrel, 15 said barrel having a semi-annular groovein one face communicating with one of said conduits, and a secondsemi-annular groove of the same radius communicating with the otherconduit, an annular groove surrounding said semi-annular groovesand'communicating with the cylinders in saidbarrel, a valve plate havingports for cooperating with said grooves to control the fiow of liquidbetween the barrel cylinders and the conduits, and a hub on saidstationary shaft between its support and said plate.

' 17-. In a well drilling system, a hydraulic machine of the swash platetype, a pair of spaced supports, a stationary shaft in one of saidsupports, a stub shaft alined with said stationary shaft and iournaledin the other of said supports,-

a hub journaled on the free end of said stationary shaft and secured tosaid stub shaft, a cylinder barrel secured to said stationary shaft, 9.second hub journaled on said stationary shaft between its support andthe cylinder barrel, a drum mounted on said hubs and forming therewith afluid-tight enclosure forsaid barrel, an angle box secured to said drum,a swash plate trunnioned in said stationary shaft, pistons reciprocallymounted in said barrel and connected with said plate, said stationaryshaft having conduits therein for transmitting work fluid to and fromsaid barrel and a valve plate secured to said drum for controlling thefiow of fluid thru said conduits.

secured to said head and journaled in the other 18. In a hydraulic motorhoisting unit of the swash plate type, a stationary shaft fixedlysupported on one end, a winding drum journaled on said shaft, a cylinderbarrel fixed to said. shaft intermediate the ends of the drum, a swashplate pivoted to said shaft for cooperating with said barrel, an anglebox forming one end of the drum and cooperating with said swash plate,and a valve plate forming the other end of the drum, said shaft havingbores from the fixed end for conducting operating fluid to and from thecylinder barrel.

19. In combination with a winding drum, a hydraulic motor of the swashplate type including a shaft fixedly supported on one end, and acylinder barrel fixed to said shaft, said shaft having bores thereinfrom said one end to said barrel, one end of said drum consisting of avalve plate for controlling the fiow of fluid between said bores and thecylinders in said barrel, said winding drum forming the enclosing shellfor said motor.

20. In a well drilling system, a hydraulic machine of the swash platetype adapted to operate as a pump when mechanically driven or as a motorwhen hydraulicly driven and comprising a support, a shaft fixedlysecured to said support, a swash plate and a cylinder barrel secured tosaid shaft, a cylindrical housing Journaled at one end on said shaft andenclosing said barrel and said swash plate, an angle box pivoted in saidhousing for cooperatingwith the swash plate, a

therein for conducting actuating fluid to said pressure responsivemeans.

' VICTOR W. ZILEN.

